Fluid pump

ABSTRACT

A FLUID PUMP MOUNTED ON A ROTATING SHAFT CAPABLE OF PUMPING TWO DIFFERENT FLUIDS INDEPENDENTLY HAVING MULTIPLE AXIALLY RECIPROCATING, RADIALLY SPACED BALL PISTONS, DRIVEN IN HARMONIC MOTION BY ROTATING REACTION CAMS PROVIDING MULTIPLE STROKES PER REVOLUTION.

May 23, 1972 v. M. PANARlTl FLUID PUMP 4 Sheets-Sheet 1 Filed Sept. '1,1970 INVENTOR VI KTOR M. PA NARfTl y 1972 v. M. AAAAAA Tl 3,664,772

F L U I D P U MP 4 Sheets-Sheet 2 Filed Sept 4 1970 NNNNNN OR VIKTOR M.PANARITI V. M. PANARITI FLUID PUMP May 23, 1972 FIG? INVENT VIKTOR M. PANA RI United States Patent O 3,664,772 FLUID PUMP Viktor MitrushiPanariti, 111 Imperial Heights Drive, Ormond Beach, Fla. 32074 FiledSept. 4, 1970, Ser. No. 69,590 Int. Cl. F04b 1/12, 19/00, 23/04 U.S. Cl.417-486 3 Claims ABSTRACT OF THE DISCLOSURE A fluid pump mounted on arotating shaft capable of pumping two different fluids independentlyhaving multiple axially reciprocating, radially spaced ball pistons,driven in harmonic motion by rotating reaction cams providing multiplestrokes per revolution.

SUMMARY OF THE INVENTION My invention provides an improved method fortransforming rotary shaft power into a reciprocating axial motion of adouble ball piston without crank shaft and connecting rods. The pumpconsists of a solid housing journaled on a rotating shaft enclosing twoseparate pumping chambers. The housing consists of two end plates inwhich are mounted oppositely biased axially aligned check valves whichfunction as an inlet and an outlet to each of the pumping chambers.Separating the two pumping chambers is a fixed cylinder block containingseveral axially aligned cylinders connecting the two pumping chambers.Slideably and sealably mounted in each of these cylinders are two freerolling balls. Fixedly mounted on the rotating shafts are two reactioncams, one on each side of the cylinder block aligned so the respectivecamming surfaces are in rolling contact with one of the balls of thedouble ball pistons. The high points of one cam surfaceare alignedopposite the low points of the other cam. As the shaft and the camsrotate the balls roll on the cam surfaces causing the double ballpistons to reciprocate axially which in turn causes the volumes of thepumping chambers to increase and decrease periodically. It is thisincreasing and decreasing chamber volume which provides the differentialpressure necessary to operate the check valves in their proper sequenceand to independently pump liquid in and out of the chambers.

For any given shaft velocity, the displacement of the pump can be variedby varying the numbenof camming slopes, number and size of balls anddiameter of the pump. This feature gives great flexibility of design ofthe pump to achieve a large variety of pumping rates for any given shaftvelocity. Since each reaction cam can have a number of high points, thepump is provided with multiple reciprocating strokes per revolutiom Thesimplicity of the design makes construction economical and maintenanceeasy.

In a preferred embodiment the pump with an internal chamber diameter ofonly seven inches provides a pumping rate of 4,317 gallons per minute,with a shaft rotating at 3,600 rpm.

Other features and advantages of this invention will be apparent fromthe following description of certain embodiments thereof taken inconjunction with the drawings.

3,664,772 Patented May 23, I972 ice FIG. 1 is a perspective of the fluidpump completely assembled.

FIG. 2 is an exploded view of the same pump with the cams and ballsshown together for clarity.

FIG. 3 is a side section taken along lines 33 of FIG. 1.

FIG. 4 is a front section taken along lines 4-4 of FIG. 3.

FIG. 5 is a perspective of a first alternative form of the pump whereinthe intake and discharge ports are rearranged.

FIG. 6 is a side section view taken on lines 6-6 of FIG. 5. I

FIG. 7 is a front section taken on lines 7-7 of FIG. 6.

FIG. 8 is a section of a second alternative form of the pump wherein thecylinder and balls revolve past stationary cams.

FIG. 9 is a front section taken on lines 99 of FIG. 8.

FIG. 10 is a section of a third alternative form wherein the ballstravel radially rather than axially.

FIG. 11 is a section taken on lines 11-11 of FIG. 10.

DESCRIPTION OF THE PREFERRED I EMBODIMENT Construction of the pump Asolid housing, 20, encloses two separate pumping chambers 21 and 22. Onit is journaled a rotating shaft 40 by means of bearings 30. The housingconsists of three parts: two identical end plates 23, and a cylinderblock 24. Each of the end plates contains a pair of oppositely biasedinlet and outlet check valves, 25, mounted axially as shown. One valveof each pair is spaced degrees away from its mate.

Several cylinder bores, 26, are drilled completely through the cylinderblock and placed around the circumference of a circle. The cylinderblock 24 is provided with axially extending flanges at its outerperimeter so that the assembled housing encloses the two hollow pumpingchambers 21 and 22.

Slideably and sealably mounted in each cylinder 26 are two balls 27,each allowed to roll freely within the cylinder. When the'double ballpistons are placed in the cylinders, the two pumping chambers areisolated by the sealing rings, 28, so that no fluid will pass betweenthem. Fixedly mounted on the shaft on opposite sides of the cylinderblock are two cylindrical reaction earns, 31 and 32, each with an equalnumber of high, 33, and low, 34, points as shown in perspective view,FIG. 2. As mentioned earlier, cam 33 is shown in FIG. 2 adjacent theballs although its actual position is on the other side of cylinderblock 24. The cam surfaces face one another with high points of onebeing aligned opposite the low points of the other. Each of the camsurfaces has rolling contact with the balls of the double ball pistonson its side of the cylinder block. As the cams rotate, the ball pistonswill reciprocate in their cylinders a number of times for eachrevolution of the cam.

Operation of the pump The shaft rotates under the power of a suitablemotor force (not shown). As the shaft, 40, rotates, cams, 32 and 33,which are fixed to the shaft also rotate. (FIG. 3 shows the layout ofthe two cams, the cylinder block, the ball pistons and the check valvesin their relationship as they cooperate during operation of the pump.The high point on cam 32 is in frictional rolling contact with one ofthe balls of the double ball pistons. A low point on cam 33 is infrictional rolling contact with the other ball of the double ballpistons. The cylinder block is fixed with respect to the moving cams. Asthe two cams begin to move together, the ball which is resting on thehigh point of cam 17 begins to roll down into the next adjacent valley.The ball which is rolling in the low point of the cam 33 begins to rollup the next adjacent high point. The rolling cam surfaces transfer anaxial force to the double ball pistons which causes the double ballpistons to move axially in the cylinders. As the many high and lowpoints on the cams roll past the pistons, the pistons reciprocate in thecylinders many times for each revolution of the cams.

As can be seen from FIG. 2, all of the pistons move together in the samedirection. As the pistons move to the right, the volume in the righthand pumping chamber decreases. This decrease in volume causes acorresponding increase in fiuid pressure which operates the outlet checkvalve for that chamber and forces fluid out of the pumping chamber intothe fluid stream. As the volume in the right hand chamber decreases, thevolume in the left hand chamber increases, causing a correspondingpressure drop which opens the inlet check valves allowing fluid to enterthe left hand pumping chamber from the fluid stream. As the pistons moveto the left, the operation is reversed. It is this periodic change involume of the two pumping chambers that provides the pumping action onthe fluid. Since the two pumping chambers are isolated from one anotherby means of the sealing rings on the ball pistons, the pump is capableof pumping two separate fluids.

MODIFICATIONS OF THE PREFERRED EMBODIMENT The first alternative form ofthe pump shown in FIGS. 5, 6 and 7 varies only in having a two wayshuttle valve 35 connected to a single intake port 37 and a two wayshuttle valve 36 connected to a single discharge port 38.

A second alternative form shown in FIGS. 8 and 9 utilizes a stationarycam element 41 as part of the end plates 43 and 44. The shaft 40 turnscylinder block 45 past these cams.

A third alternative form of the pump is shown in FIGS. and 11. Like thesecond alternative form cylinder block 46 revolves while internal cam 47and external cam 48 are stationary. The ball pistons 49 reciprocateradially to effect their pumping action while being revolved around theaxis in the cylinder block 46.

Each valve 35 and 36 is connected to each pumping chamber. Inlet shuttlevalve 35 prevents back flow during the compression stage of each chamberwhile allowing the other chamber to fill during the expansion stage.Discharge shuttle valve 36 allows fluid to pass from the chamber in itscompression stage but not to flow back into the chamber being filled inits expansion stage.

(Any of the foregoing versions of the pump may be used to pump twoentirely separate fluids provided that adequate provision is made forfluid seal within the cylinder bore. The drawings disclose aconventional ring seal 28 which may be utilized. Equivalent seals whichmay also physically separate the two ball pistons are well known and mayalso be utilized.

Another feature is that the check valve or shuttle valve may beeliminated and a sliding port valving arrangement may be substituted. 7

Having disclosed my invention in the foregoing specification, I claim:

1. A positive displacement fluid pump (a) two internal fluid chambers,

(b) a cylinder block having a plurality of cylinder bores,

(c) opposite ends of said cylinder bores communicating with said twointernal fluid chambers,

(d) apair of synchronized cooperating cam tracks, each track placed onopposite sides of said cylinder block within each chamber and facing theends of said cylindrical bores,

(e) a pair of piston balls displaced within each of said bores, each ofsaid balls cooperating with one of said cam tracks,

(f) said cam tracks and cylinder block in relative rotational motion,

(g) said relative rotational motion provided by a powered shaft for saidpump,

(h) said relative rotational movement providing linear movement of saidballs within said cylinder bores,

(i) said linear movement of said balls providing cyclical expansion andcontraction of each of said fluid chambers whereby a pumping action iseffected,

2. The fluid pump of claim 1 wherein a single ball is displaced in eachcylinder bore and acted upon by each cam in each chamber.

3. In the fluid pump of claim 1 a shuttle valve connected to bothchambers, thereby providing a continuous flow of fluid through onedischarge or intake port.

References Cited UNITED STATES PATENTS 3,403,668 10/ 1968 Schottler417-486 X 3,415,059 12/1968 Foster et al. 417-486 X ROBERT M. WALKER,Primary Examiner US. Cl. X.R.

